Large-torque high-speed blade swing motor servo system for aircraft landing gear test

Abstract

The invention relates to the technical field of aircraft landing gear tests, and particularly discloses a large-torque high-speed blade swing motor servo system for aircraft landing gear tests, which is characterized in that an oil source conveys hydraulic oil in a recovery oil tank into an energy accumulator group, and the energy accumulator group is communicated with a first port of a servo valve; a second port of the servo valve is communicated with an oil liquid input port of the recovery oil tank, a third port of the servo valve is communicated with a first oil liquid conveying port of the blade motor assembly, and a fourth port of the servo valve is communicated with a second oil liquid conveying port of the blade motor assembly. High-pressure hydraulic oil in the energy accumulator set is input into the blade motor assembly and then output, precise control over the swing start, the swing angle and the rotating speed of the blade motor assembly is achieved, a large amount of high-pressure hydraulic oil is rapidly released through the energy accumulator set, and the instantaneous flow of the system is sharply increased; and the rotating speed and the torque value of the blade motor assembly can be greatly increased in a short time, so that the power of the motor reaches extremely high peak power.

Description

Technical Field

[0001] The invention relates to the technical field of aircraft landing gear testing, and in particular to a high-torque high-speed blade swing motor servo system for aircraft landing gear testing. Background Art

[0002] The dynamic response of aircraft landing gear during approaching the runway, taxiing and braking is one of the important topics in the study of aircraft landing gear dynamics, and it mainly studies the dynamic characteristics of the landing gear structure during approaching the runway, taxiing and braking.

[0003] After the aircraft landing gear system is developed, it needs to be tested and simulated in advance to verify whether the function of the landing gear meets the index requirements.

[0004] When simulating the instantaneous state of the aircraft landing gear touching the ground, water pressure can be used to impact the trolley carrying the landing gear for testing. The water pressure is generally controlled by the opening or closing of a large valve, and the opening or closing of the large valve can be controlled by a servo swing motor system.

[0005] The existing motor system is a motor connected to a reducer to drive the components to swing, a reversing valve and a throttle valve are used to control the motor, and a large-flow oil source is used to supply oil to the system.

[0006] Therefore, the hydraulic motor system of the prior art adopts a multi-stage reduction transmission mode, which results in high torque and low speed, or low torque and high speed, and the two cannot be achieved at the same time.

[0007] Controlled by reversing valve and throttle valve will result in inaccurate motor stop position and large impact, while a large flow oil source will be configured to increase the speed, which will also result in the disadvantages of low peak power and high system energy consumption.

[0008] Based on the above problems, how to make the peak power of the hydraulic motor system high and the system energy consumption low is a problem that needs to be solved urgently. Summary of the invention

[0009] In view of the technical problems in the prior art, the present invention provides a high-torque and high-speed blade swing motor servo system for aircraft landing gear testing.

[0010] The present invention discloses a high-torque and high-speed blade swing motor servo system for aircraft landing gear testing, wherein the motor servo system comprises an oil source, an accumulator group, a servo valve, a blade motor assembly, a recovery oil tank and a valve controller, wherein: The oil input port and the oil output port of the oil source are respectively connected with the recovery oil tank and the accumulator group through hydraulic pipelines, and the oil source is used to transport the hydraulic oil in the recovery oil tank to the accumulator group; The oil output port of the accumulator group is connected to the first port of the servo valve through a hydraulic pipeline; The second port of the servo valve is connected to the oil input port of the recovery tank through a hydraulic pipeline; the third port of the servo valve is connected to the first oil delivery port of the vane motor assembly through a hydraulic pipeline; the fourth port of the servo valve is connected to the second oil delivery port of the vane motor assembly through a hydraulic pipeline; The valve controller is electrically connected to the servo valve and is used to control the connectivity status and valve opening of the servo valve. When the first port and the third port of the servo valve are connected and the second port and the fourth port are connected, the first oil delivery port of the vane motor assembly is the oil input port and the second oil delivery port is the oil output port; when the first port and the fourth port of the servo valve are connected and the second port and the third port are connected, the first oil delivery port of the vane motor assembly is the oil output port and the second oil delivery port is the oil input port.

[0011] Furthermore, the vane motor assembly includes a first vane motor, a second vane motor and a swinging main shaft, and the motor shafts of the first vane motor and the second vane motor are respectively coaxially fixedly connected to the two ends of the swinging main shaft; the first vane motor and the second vane motor are both provided with a first oil delivery port and a second oil delivery port, and the third port of the servo valve is connected to the first oil delivery port of the first vane motor and the second vane motor through a hydraulic pipeline; the fourth port of the servo valve is connected to the second oil delivery port of the first vane motor and the second vane motor through a hydraulic pipeline, so that the first vane motor and the second vane motor are in a parallel relationship.

[0012] Further, the accumulator group includes a motor oil accumulator and a motor oil switch valve, wherein: The oil output port of the oil source is connected to the motor oil accumulator through a hydraulic pipeline, and is used to transport the hydraulic oil in the recovery tank to the motor oil accumulator; The motor oil accumulator is connected to the first port of the servo valve through a hydraulic pipeline; the motor oil switch valve is arranged on the hydraulic pipeline between the motor oil accumulator and the first port of the servo valve; The valve controller is electrically connected to the motor oil switch valve and is used to control the connection state and valve opening of the motor oil switch valve.

[0013] Furthermore, the accumulator group also includes a pilot oil accumulator and a pilot oil switch valve, wherein: The oil output port of the oil source is connected to the motor oil accumulator and the pilot oil accumulator in sequence through a hydraulic pipeline. A first one-way valve is provided between the motor oil accumulator and the pilot oil accumulator, and the oil flows in a direction from the motor oil accumulator to the pilot oil accumulator. The pilot oil accumulator is connected to the control input port of the servo valve through a hydraulic pipeline; the pilot oil switch valve is arranged on the hydraulic pipeline between the pilot oil accumulator and the control input port of the servo valve; The control output port of the servo valve is connected to the recovery oil tank through a hydraulic pipeline; The valve controller is electrically connected to the pilot oil switch valve and is used to control the connection state and valve opening of the pilot oil switch valve.

[0014] Furthermore, the accumulator group also includes a unloading throttle valve and an unloading solenoid valve, wherein: The motor oil accumulator is connected to the recovery oil tank through a hydraulic pipeline, and the unloading throttle valve and the unloading solenoid valve are sequentially arranged on the hydraulic pipeline between the motor oil accumulator and the recovery oil tank; The valve controller is electrically connected to the unloading throttle valve and the unloading solenoid valve respectively, and is used for controlling the connection state and valve opening of the unloading throttle valve and the unloading solenoid valve.

[0015] Furthermore, the accumulator group also includes an oil supply valve and a manual unloading valve, wherein: The oil supply valve is arranged on the hydraulic pipeline between the oil output port of the oil source and the oil accumulator for the motor; the valve controller is electrically connected to the oil supply valve and is used to control the connection state and valve opening of the oil supply valve; The motor oil accumulator is connected to the output end of the unloading solenoid valve through a hydraulic pipeline. The manual unloading valve is arranged on the hydraulic pipeline from the motor oil accumulator to the output end of the unloading solenoid valve, and the manual unloading valve is in a normally closed state.

[0016] Furthermore, the motor servo system further comprises a first safety valve, a second safety valve and a third safety valve, wherein: The first safety valve is arranged on the first pipeline, and the two ends of the first pipeline are respectively connected to the motor oil accumulator and the oil input port of the recovery tank; The second safety valve is arranged on the second pipeline, and the two ends of the second pipeline are respectively connected to the third port of the servo valve and the oil input port of the recovery tank; The third safety valve is arranged on the third pipeline, and two ends of the third pipeline are respectively connected to the fourth port of the servo valve and the oil input port of the recovery oil tank.

[0017] Furthermore, the motor servo system further includes a first pressure sensor, a second pressure sensor, and a third pressure sensor, wherein: The first pressure sensor is located on a hydraulic pipeline connected to the motor oil accumulator and is used to detect the oil pressure of the motor oil accumulator; The second pressure sensor is located on the hydraulic pipeline connected to the first oil delivery port of the vane motor assembly, and is used to detect the oil pressure of the first oil delivery port of the vane motor assembly; The third pressure sensor is located on the hydraulic pipeline connected to the second oil delivery port of the vane motor assembly, and is used to detect the oil pressure of the second oil delivery port of the vane motor assembly; The valve controller is electrically connected to the first pressure sensor, the second pressure sensor, and the third pressure sensor.

[0018] Furthermore, the lengths of the hydraulic pipelines from the third port of the servo valve to the first oil delivery ports of the first vane motor and the second vane motor are equal, and the lengths of the hydraulic pipelines from the fourth port of the servo valve to the second oil delivery ports of the first vane motor and the second vane motor are equal, so that the hydraulic oil supplied by the servo valve to the first vane motor and the second vane motor arrives at the same time.

[0019] Furthermore, the first vane motor and the second vane motor each include a cylinder body and a motor shaft, the motor shaft passes through the cylinder body, a plurality of fixed blades are provided at intervals on the inner wall of the cylinder body, and moving blades are provided on the motor shaft and are respectively located between two adjacent fixed blades, each of the moving blades divides the cavity between two adjacent fixed blades into a first oil chamber and a second oil chamber, and the first oil chambers and the second oil chambers in the cylinder body are alternately arranged, the first oil delivery port is connected to the first oil chamber, and the second oil delivery port is connected to the second oil chamber.

[0020] The invention discloses a high-torque high-speed blade swing motor servo system for aircraft landing gear testing. The oil source is used to deliver the hydraulic oil in the recovery tank to the accumulator group. The oil output port of the accumulator group is communicated with the first port of the servo valve through a hydraulic pipeline. The second port of the servo valve is communicated with the oil input port of the recovery tank through a hydraulic pipeline. The third port is communicated with the first oil delivery port of the blade motor assembly through a hydraulic pipeline. The fourth port is communicated with the second oil delivery port of the blade motor assembly through a hydraulic pipeline. Under the control of the valve controller on the connection state and valve opening of the servo valve, the high-pressure hydraulic oil in the accumulator group is input into the blade motor assembly and then output. This not only realizes the precise control of the start, swing angle and rotation speed of the blade motor assembly, but also quickly releases a large amount of high-pressure hydraulic oil through the accumulator group, and the instantaneous flow of the system increases sharply. In a short time, the speed and torque of the blade motor assembly can be greatly increased, so that the power of the motor reaches an extremely high peak power. The oil source is used to deliver oil to the accumulator group, and it can be closed after the pressure accumulation is completed. It does not need to work for a long time, which also plays a role in energy saving and makes the system energy consumption lower. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0022] Figure 1 This is a module composition diagram of a high-torque, high-speed blade swing motor servo system for aircraft landing gear testing according to an embodiment of the present invention; Figure 2 This is a structural diagram of a high-torque, high-speed blade swing motor servo system for aircraft landing gear testing according to an embodiment of the present invention; Figure 3 It is a structural schematic diagram of a high-torque and high-speed blade swing motor servo system for aircraft landing gear testing according to an embodiment of the present invention; Figure 4 A schematic diagram of the structure of a vane motor according to an embodiment of the present invention; Figure 5 It is a simulation hydraulic principle diagram of an embodiment of the present invention; Figure 6 The motor start-stop curve simulated and analyzed in the embodiment of the present invention; Figure 7 The servo valve flow curve simulated and analyzed in the embodiment of the present invention; Figure 8 is a curve of outlet pressure variation of the accumulator group simulated and analyzed in an embodiment of the present invention; Fig. 9 The effective working volume curve of the accumulator group simulated and analyzed in the embodiment of the present invention; Among them, 10-oil source, 20-accumulator group, 201-motor oil accumulator, 202-motor oil switch, 203-pilot oil accumulator, 204-pilot oil switch valve, 205-first one-way valve, 206-unloading throttle valve, 207-unloading solenoid valve, 208-oil supply valve, 209-manual unloading valve, 30-servo valve 40-vane motor assembly, 401-first vane motor, 402-second vane motor, 403-swing spindle, 404-cylinder body, 405-motor shaft, 50-recovery oil tank, 60-valve controller, 701-first safety valve, 702-second safety valve, 703-third safety valve, 801-first pressure sensor, 802-second pressure sensor, 803-third pressure sensor. DETAILED DESCRIPTION

[0023] The technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments.

[0024] Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in the field without making any creative work shall fall within the protection scope of the present invention.

[0025] A high-torque high-speed blade swing motor servo system for aircraft landing gear testing according to an embodiment of the present invention is provided. Figures 1 to 3As shown, the motor servo system includes an oil source 10, an accumulator group 20, a servo valve 30, a vane motor assembly 40, a recovery tank 50 and a valve controller 60, wherein: the oil input port and the oil output port of the oil source 10 are respectively connected to the recovery tank 50 and the accumulator group 20 through hydraulic pipelines, and the oil source 10 is used to transport the hydraulic oil in the recovery tank 50 to the accumulator group 20; the oil output port of the accumulator group 20 is connected to the first port A of the servo valve 30 through a hydraulic pipeline; the second port B of the servo valve 30 is connected to the oil input port of the recovery tank 50 through a hydraulic pipeline; the third port C of the servo valve 30 is connected to the first oil delivery port of the vane motor assembly 40 through a hydraulic pipeline; the fourth port D of the servo valve 30 is connected to the second oil delivery port of the vane motor assembly 40 through a hydraulic pipeline; the valve controller 60 is electrically connected to the servo valve 30, and is used to control the connection state and valve opening of the servo valve 30.

[0026] In an embodiment of the present invention, when the first port A and the third port C of the servo valve 30 are connected, and the second port B and the fourth port D are connected, the first oil delivery port of the vane motor assembly 40 is the oil input port, and the second oil delivery port is the oil output port. In this state, the high-pressure hydraulic oil in the accumulator group 20 is input from the first port A of the servo valve 30 and output from the third port C, and directly reaches the first oil delivery port of the vane motor assembly 40 through the hydraulic pipeline. After entering the vane motor assembly 40, the vanes rotate in the first direction. The hydraulic oil is then output from the second oil delivery port of the vane motor assembly 40, enters the servo valve 30 from the fourth port D of the servo valve 30 through the hydraulic pipeline, and then outputs from the second port B of the servo valve 30, and is delivered to the recovery tank 50 through the hydraulic pipeline. This state can be set as the oil circuit control mode when the large valve is in the closed state.

[0027] When the first port A and the fourth port D of the servo valve 30 are connected, and the second port B and the third port C are connected, the first oil delivery port of the vane motor assembly 40 is the oil output port, and the second oil delivery port is the oil input port. In this state, the high-pressure hydraulic oil in the accumulator group 20 is input from the first port A and output from the fourth port D of the servo valve 30, and directly reaches the second oil delivery port of the vane motor assembly 40 through the hydraulic pipeline. After entering the vane motor assembly 40, the vanes rotate in the second direction. The hydraulic oil is then output from the first oil delivery port of the vane motor assembly 40, enters the servo valve 30 from the third port C of the servo valve 30 through the hydraulic pipeline, and then outputs from the second port B of the servo valve 30, and is delivered to the recovery tank 50 through the hydraulic pipeline. This state can be set as the oil circuit control mode when the large valve is in the open state.

[0028] The valve controller 60 controls the connectivity of the servo valve 30, and can control the start and direction of rotation of the vanes in the vane motor assembly 40, thereby controlling the start, direction and angle of motor swing. By controlling the valve opening of the servo valve 30, the pressure and flow of the hydraulic oil entering the vane motor assembly 40 can be controlled, so the rotation speed of the vanes in the vane motor assembly 40 can be controlled, thereby controlling the motor swing speed.

[0029] In summary, in this embodiment, the valve controller 60 is used to control the connectivity status and valve opening of the servo valve 30, so as to realize the pressure and flow control of the hydraulic oil input into the vane motor assembly 40, so as to accurately control the motor's swing angle, rotation speed, acceleration and deceleration time and other parameters. The specific control parameters can be realized by setting the control program according to actual needs, and this embodiment does not make any specific limitations.

[0030] The servo valve 30 of the present embodiment is a key component for controlling the vane motor assembly 40 , and can accurately control the pressure flow provided to the vane motor assembly 40 , and has the characteristics of large flow and fast response.

[0031] The recovery oil tank 50 is used to store the return oil of the system.

[0032] It should be particularly noted that the oil source 10 in the embodiment of the present invention uses a small flow oil source to reduce the system cost as much as possible on the basis of achieving the system function.

[0033] Before the system is officially used, the accumulator group 20 is filled with oil through a small flow oil source. After the filling is completed, the system can be shut down without having to work for a long time.

[0034] In the system of the embodiment of the present invention, most of the power consumption is generated by the oil source transferring oil to the accumulator group 20. The oil source 10 is used to store high-pressure hydraulic oil for the accumulator group 20, and it can be turned off after the pressure accumulation is completed, which plays a role in energy saving. Furthermore, a motor product with a power of 7.5KW can be used to drive a small flow oil source to reduce energy consumption as much as possible on the basis of meeting the pressure storage requirements.

[0035] When the system is officially running, the accumulator group 20 quickly releases a large amount of high-pressure hydraulic oil, and the system's instantaneous flow rate increases sharply, reaching 3300L / min. In a short period of time, the speed and torque of the vane motor assembly 40 can be greatly increased, and the power generated by the motor is as high as 643kW, so the motor power can reach an extremely high peak power.

[0036] Specifically, Figure 2 and Figure 3As shown, the vane motor assembly 40 in this embodiment includes a first vane motor 401, a second vane motor 402 and a swinging main shaft 403, and the motor shafts of the first vane motor 401 and the second vane motor 402 are respectively coaxially fixedly connected to the two ends of the swinging main shaft 403; the first vane motor 401 and the second vane motor 402 are both provided with a first oil delivery port and a second oil delivery port, and the third port of the servo valve 30 is connected to the first oil delivery port of the first vane motor 401 and the second vane motor 402 through a hydraulic pipeline; the fourth port of the servo valve 30 is connected to the second oil delivery port of the first vane motor 401 and the second vane motor 402 through a hydraulic pipeline, so that the first vane motor 401 and the second vane motor 402 are in a parallel relationship.

[0037] In an embodiment of the present invention, a "spline" can be used to achieve a coaxial fixed connection between the motor shafts of the first blade motor 401 and the second blade motor 402 and the two ends of the swing main shaft 403. The first blade motor 401 and the second blade motor 402 act as actuators to directly drive the swing main shaft 403 to swing, so the motor speed is the speed of the swing main shaft 403, and the swing torque of the motor is greater. The displacement of a single motor is approximately 4583 ml / rad. In the initial state, the parallel torque of the two motors can reach 200,000 Nm, and the speed is relatively small at this time. When the two motors rotate stably, the parallel torque can reach 110,000 Nm, and the speed reaches 335° / s. Therefore, the design of this system makes the swing main shaft 403 have a fast speed, large torque, high peak power and low system energy consumption.

[0038] In this embodiment, two vane motors are connected in parallel to jointly drive the swing main shaft 403 to swing. The shape of the swing main shaft 403 can be designed according to the required structure, which is not specifically limited in this embodiment.

[0039] In addition, the embodiment of the present invention does not limit the specific structure of the first vane motor 401 and the second vane motor 402. Preferably, Figure 4 As shown, the first vane motor 401 and the second vane motor 402 in the embodiment of the present invention both include a cylinder body 404 and a motor shaft 405, the motor shaft 405 passes through the cylinder body 404, a plurality of fixed blades Y are provided at intervals on the inner wall of the cylinder body 404, and movable blades X are provided on the motor shaft 405 and are respectively located between two adjacent fixed blades Y, each movable blade X divides the cavity between two adjacent fixed blades Y into a first oil cavity and a second oil cavity, and the first oil cavities and the second oil cavities in the cylinder body 404 are alternately arranged, the first oil delivery port is connected to the first oil cavity, and the second oil delivery port is connected to the second oil cavity.

[0040] As an example, a three-blade motor may be used, such as Figure 4As shown, each motor has 6 working chambers, which are respectively denoted as A1, A2, A3, B1, B2, and B3, wherein A1, A2, and A3 are the aforementioned first oil chambers, and B1, B2, and B3 are the aforementioned second oil chambers. No matter whether the hydraulic oil is input into the A1, A2, and A3 chambers or into the B1, B2, and B3 chambers, the moving blades X in the figure will drive the motor shaft 405 to rotate in the cylinder body 404 under the action of the high-pressure hydraulic oil, and the rotation direction is divided into clockwise rotation and counterclockwise rotation. The stationary blades Y will limit the rotation angle of the moving blades X, so that the moving blades X can realize the continuous switching of clockwise / counterclockwise rotation, forming a swing effect on the swing main shaft 403.

[0041] Since the first vane motor 401 and the second vane motor 402 in the embodiment of the present invention are controlled by a servo valve 30 at the same time, it is preferred to perform the following "symmetrical piping" design: the length of the hydraulic pipeline from the third port of the servo valve 30 to the first oil delivery port of the first vane motor 401 and the second vane motor 402 is equal, and the length of the hydraulic pipeline from the fourth port of the servo valve 30 to the second oil delivery port of the first vane motor 401 and the second vane motor 402 is equal, so that the hydraulic oil supplied by the servo valve 30 to the first vane motor 401 and the second vane motor 402 arrives at the same time; in this way, the control oil from the servo valve 30 can reach the loading chamber of the motor at the same time, avoiding different impacts, resulting in load imbalance and motor overload.

[0042] More preferably, a hose is selected for the hydraulic pipeline directly connected to the first blade motor 401 and the second blade motor 402, because the operation of the motor will generate vibration and impact, and the hose can effectively absorb these vibrations and impacts. The hydraulic pipelines in the remaining positions can use hard pipes, because the design of the embodiment of the present invention needs to provide a larger flow rate, and the hard pipe can provide better protection and support. Each pipeline is fixed in the corresponding position by a pipe clamp to ensure the normal operation of the system.

[0043] Specifically, Figure 2 As shown, the accumulator group 20 includes a motor oil accumulator 201 and a motor oil switch valve 202, wherein: the oil output port of the oil source 10 is connected to the motor oil accumulator 201 through a hydraulic pipeline, which is used to transport the hydraulic oil in the recovery tank 50 to the motor oil accumulator 201; the motor oil accumulator 201 is connected to the first port of the servo valve 30 through a hydraulic pipeline; the motor oil switch valve 202 is arranged on the hydraulic pipeline between the motor oil accumulator 201 and the first port of the servo valve 30; the valve controller 60 is electrically connected to the motor oil switch valve 202, which is used to control the connection state and valve opening of the motor oil switch valve 202.

[0044] The motor oil accumulator 201 in the embodiment of the present invention may include multiple motor oil accumulators 201 to increase the total oil pressure.

[0045] Specifically, Figure 2 As shown, the accumulator group 20 also includes a pilot oil accumulator 203 and a pilot oil switch valve 204, wherein: the oil output port of the oil source 10 is connected to the motor oil accumulator 201 and the pilot oil accumulator 203 in sequence through a hydraulic pipeline, a first one-way valve 205 is provided between the motor oil accumulator 201 and the pilot oil accumulator 203, and the oil flow direction is from the motor oil accumulator 201 to the pilot oil accumulator 203; the pilot oil accumulator 203 is connected to the control input port of the servo valve 30 through a hydraulic pipeline; the pilot oil switch valve 204 is provided on the hydraulic pipeline between the pilot oil accumulator 203 and the control input port of the servo valve 30; the control output port of the servo valve 30 is connected to the recovery oil tank 50 through a hydraulic pipeline; the valve controller 60 is electrically connected to the pilot oil switch valve 204, and is used to control the connection state and valve opening of the pilot oil switch valve 204.

[0046] The hydraulic oil stored in the motor oil accumulator 201 in the embodiment of the present invention is mainly oil for motor swinging, and the hydraulic oil outputted is high-pressure oil, and can also supplement the possible pressure shortage of the pilot oil accumulator 203.

[0047] The hydraulic oil stored in the pilot oil accumulator 203 is used to supply oil to the pilot oil port of the servo valve 30 separately, so as to prevent the pilot oil pressure from fluctuating and affecting the control of the servo valve 30 .

[0048] The motor oil switch valve 202 and the pilot oil switch valve 204 are switch valves for supplying oil to the motor and the pilot oil port of the servo valve 30 respectively. The hydraulic oil in the pilot oil accumulator 203 supplies oil to the servo valve 30 through the pilot oil switch valve 204. At the same time, under the control of the valve controller 60, the servo valve 30 is controlled to be located at the left position, the right position and between the left and right positions to prevent leakage in the motor and the servo valve 30 when the motor does not need to swing, causing a pressure drop in the motor oil accumulator 201 and the pilot oil accumulator 203.

[0049] Specifically, Figure 2 As shown, the accumulator group 20 also includes a unloading throttle valve 206 and an unloading solenoid valve 207, wherein: the motor oil accumulator 201 is connected to the recovery tank 50 through a hydraulic pipeline, and the unloading throttle valve 206 and the unloading solenoid valve 207 are sequentially arranged on the hydraulic pipeline between the motor oil accumulator 201 and the recovery tank 50; the valve controller 60 is electrically connected to the unloading throttle valve 206 and the unloading solenoid valve 207, respectively, for controlling the connection state and valve opening of the unloading throttle valve 206 and the unloading solenoid valve 207.

[0050] The unloading solenoid valve 207 is controlled by the valve controller 60, so it is an electrically controlled valve for unloading the motor oil accumulator 201. The unloading throttle valve 206 can adjust the unloading flow under the control of the valve controller 60 to prevent the unloading impact from being too large and damaging the recovery oil tank 50.

[0051] Specifically, Figure 2 As shown, the accumulator group 20 also includes an oil supply valve 208 and a manual unloading valve 209, wherein: the oil supply valve 208 is arranged on the hydraulic pipeline between the oil output port of the oil source 10 and the motor oil accumulator 201; the valve controller 60 is electrically connected to the oil supply valve 208, and is used to control the connection state and valve opening of the oil supply valve 208; the motor oil accumulator 201 is connected to the output end of the unloading solenoid valve 207 through a hydraulic pipeline, and the manual unloading valve 209 is arranged on the hydraulic pipeline between the motor oil accumulator 201 and the output end of the unloading solenoid valve 207, and the manual unloading valve 209 is in a normally closed state.

[0052] The oil supply valve 208 in this embodiment is used to control the on-off of the hydraulic pipeline between the oil source 10 and the accumulator group 20, that is, it is a switch valve for supplying oil to the accumulator group 20. It is in a closed state when the oil source 10 is not supplying oil, and is in an open state when the oil source 10 supplies oil to the motor oil accumulator 201.

[0053] The manual unloading valve 209 in this embodiment is designed to manually unload the pressure of the motor oil accumulator 201 when the system is under maintenance or shut down.

[0054] Generally, the unloading solenoid valve 207 of the aforementioned embodiment can be used to unload the motor oil accumulator 201 . When the unloading solenoid valve 207 fails, the manual unloading valve 209 can also be used to unload the motor oil accumulator 201 .

[0055] Specifically, Figure 2 As shown, the motor servo system also includes a first safety valve 701, a second safety valve 702 and a third safety valve 703, wherein: the first safety valve 701 is arranged on the first pipeline, and the two ends of the first pipeline are respectively connected to the motor oil accumulator 201 and the oil input port of the recovery tank 50; the second safety valve 702 is arranged on the second pipeline, and the two ends of the second pipeline are respectively connected to the third port of the servo valve 30 and the oil input port of the recovery tank 50; the third safety valve 703 is arranged on the third pipeline, and the two ends of the third pipeline are respectively connected to the fourth port of the servo valve 30 and the oil input port of the recovery tank 50.

[0056] The first safety valve 701 is configured to unload when the pressure of the motor oil accumulator 201 exceeds a specified value to protect the system safety. The second safety valve 702 and the third safety valve 703 are configured to unload when the motor pressure exceeds a specified value to protect the motor.

[0057] Specifically, Figure 2 As shown, the motor servo system also includes a first pressure sensor 801, a second pressure sensor 802, and a third pressure sensor 803, wherein: the first pressure sensor 801 is located on a hydraulic pipeline connected to the motor oil accumulator 201, and is used to detect the oil pressure of the motor oil accumulator 201; the second pressure sensor 802 is located on a hydraulic pipeline connected to the first oil delivery port of the vane motor assembly 40, and is used to detect the oil pressure of the first oil delivery port of the vane motor assembly 40; the third pressure sensor 803 is located on a hydraulic pipeline connected to the second oil delivery port of the vane motor assembly 40, and is used to detect the oil pressure of the second oil delivery port of the vane motor assembly 40; the valve controller 60 is electrically connected to the first pressure sensor 801, the second pressure sensor 802, and the third pressure sensor 803, and the valve controller 60 controls the connection state and valve opening of the relevant valves according to the pressure detection values ​​of the first pressure sensor 801, the second pressure sensor 802, and the third pressure sensor 803.

[0058] The arrangement of the first pressure sensor 801, the second pressure sensor 802, and the third pressure sensor 803 in this embodiment can detect the pressure of the motor oil accumulator 201, the first oil delivery port (motor A1, A2, A3 chambers) of the vane motor assembly 40, and the second oil delivery port (motor B1, B2, B3 chambers) of the vane motor assembly 40 in the system.

[0059] Specifically, the vane motor assembly also includes a motor position detection element, which is disposed in the first vane motor 401 and / or the second vane motor 402. The motor position detection element is electrically connected to the valve controller 60. The valve controller controls the servo valve 30 based on the position detection information fed back by the motor position detection element, so that the stop position of the first vane motor 401 and the second vane motor 402 is more accurate, reducing the impact of the mechanical mechanism and achieving the effect of closed-loop control.

[0060] In addition, the present embodiment may further provide a control program to control the first vane motor 401 and the second vane motor 402 to perform acceleration and deceleration control at the initial start-up and before stopping, so as to further reduce the impact on the mechanical structure.

[0061] In combination with the above-mentioned embodiments, the working process of the system is described as follows: When the system is working, it is necessary to first use a small flow oil source to fill the accumulator group 20 with oil.

[0062] The accumulator group 20 provides motor oil and pilot oil. The motor oil can be supplemented to the pilot oil, but the pilot oil cannot enter the motor oil, thereby ensuring the priority of the pilot oil.

[0063] After the accumulator group 20 is filled with oil to a specified pressure by the small flow oil source, the system enters a stage of waiting for the motor to swing.

[0064] After the system issues a swing command, the motor oil switch valve 202 and the pilot oil switch valve 204 are in a conducting state, and the valve controller 60 controls the servo valve 30 to provide flow to the vane motor assembly 40 according to the program, and controls the swing angle, rotation speed, acceleration and deceleration time and other parameters of the first vane motor 401 and the second vane motor 402.

[0065] Preferably, the servo valve 30 can be set so that when the system suddenly loses power (when the power is off, the servo valve 30 is located in the left position under the action of the servo valve 30 spring), the hydraulic oil pressure in the accumulator group 20 can be used to automatically swing the first vane motor 401 and the second vane motor 402 to one side (the swinging side can put the large valve in a closed state). This function can be used as a system emergency protection.

[0066] As an example, the flow rate of the small flow oil source in this embodiment can be selected as 10L / min, and a 200L accumulator is used to provide transient oil supply (accumulator volume ≥ 200L can meet the requirements), and the servo valve 30 adopts large flow model parameters.

[0067] The simulation model is used to simulate and analyze the system with the above set parameters. Figure 5 The hydraulic simulation model designed and established according to this embodiment has the following simulation results: like Figure 6 and Figure 7 As shown, the opening and closing time is within 0.2s, and the maximum flow requirement of the servo valve 30 is >5900L / min. Figure 7 The red and blue colors represent the inflow and outflow directions respectively.

[0068] Accumulator group 20 outlet pressure change see Figure 8 As shown, it can be seen that after selecting the 200L accumulator group, the pressure drops to 20MPa after one opening and closing, and the intermediate oil source 10 can also slightly replenish oil, indicating that the leakage flow can be compensated and the test requirements can be met.

[0069] The simulation results of the effective working volume of the accumulator group 20 are shown in FIG9 , and the results show that the 200L accumulator group meets the valve drive requirements.

[0070] According to FIG. 9 , the maximum effective volume of the accumulator group 20 is 135 L. The accumulator group 20 is supplied with oil by the oil source 10 at a rate of 10 L / min. The oil supply time is about 10 min, which is appropriate. The present solution is feasible.

[0071] The invention discloses a high-torque high-speed blade swing motor servo system for aircraft landing gear testing. The oil source is used to deliver the hydraulic oil in the recovery tank to the accumulator group. The oil output port of the accumulator group is communicated with the first port of the servo valve through a hydraulic pipeline. The second port of the servo valve is communicated with the oil input port of the recovery tank through a hydraulic pipeline. The third port is communicated with the first oil delivery port of the blade motor assembly through a hydraulic pipeline. The fourth port is communicated with the second oil delivery port of the blade motor assembly through a hydraulic pipeline. Under the control of the valve controller on the connection state and valve opening of the servo valve, the high-pressure hydraulic oil in the accumulator group is input into the blade motor assembly and then output. This not only realizes the precise control of the start, swing angle and rotation speed of the blade motor assembly, but also quickly releases a large amount of high-pressure hydraulic oil through the accumulator group, and the instantaneous flow of the system increases sharply. In a short time, the speed and torque of the blade motor assembly can be greatly increased, so that the power of the motor reaches an extremely high peak power. The oil source is used to deliver oil to the accumulator group, and it can be closed after the pressure accumulation is completed. It does not need to work for a long time, which also plays a role in energy saving and makes the system energy consumption lower.

[0072] The present invention is further described above with the aid of specific embodiments. However, it should be understood that the specific description here should not be construed as limiting the essence and scope of the present invention. Various modifications made to the above embodiments by ordinary technicians in the field after reading this specification are all within the scope of protection of the present invention.

Claims

1. A high-torque, high-speed blade swing motor servo system for aircraft landing gear testing, characterized in that: The motor servo system includes an oil source, an accumulator group, a servo valve, a vane motor assembly, a recovery oil tank and a valve controller, wherein: The oil input port and the oil output port of the oil source are respectively connected with the recovery oil tank and the accumulator group through hydraulic pipelines, and the oil source is used to transport the hydraulic oil in the recovery oil tank to the accumulator group; The oil output port of the accumulator group is connected to the first port of the servo valve through a hydraulic pipeline; The second port of the servo valve is communicated with the oil input port of the recovery oil tank through a hydraulic pipeline; the third port of the servo valve is communicated with the first oil delivery port of the vane motor assembly through a hydraulic pipeline; the fourth port of the servo valve is communicated with the second oil delivery port of the vane motor assembly through a hydraulic pipeline; The valve controller is electrically connected to the servo valve, and is used to control the connectivity state and valve opening of the servo valve. When the first port and the third port of the servo valve are connected, and the second port and the fourth port are connected, the first oil delivery port of the vane motor assembly is the oil input port, and the second oil delivery port is the oil output port; when the first port and the fourth port of the servo valve are connected, and the second port and the third port are connected, the first oil delivery port of the vane motor assembly is the oil output port, and the second oil delivery port is the oil input port.

2. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 1, characterized in that: The vane motor assembly includes a first vane motor, a second vane motor and a swinging main shaft, the motor shafts of the first vane motor and the second vane motor are respectively coaxially fixedly connected to the two ends of the swinging main shaft; the first vane motor and the second vane motor are both provided with the first oil delivery port and the second oil delivery port, the third port of the servo valve is connected to the first oil delivery port of the first vane motor and the second vane motor through a hydraulic pipeline; the fourth port of the servo valve is connected to the second oil delivery port of the first vane motor and the second vane motor through a hydraulic pipeline, so that the first vane motor and the second vane motor are in a parallel relationship.

3. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 2, characterized in that: The accumulator group includes a motor oil accumulator and a motor oil switch valve, wherein: The oil outlet of the oil source is connected to the motor oil accumulator through a hydraulic pipeline, so as to transport the hydraulic oil in the recovery oil tank to the motor oil accumulator; The motor oil accumulator is connected to the first port of the servo valve through a hydraulic pipeline; the motor oil switch valve is arranged on the hydraulic pipeline between the motor oil accumulator and the first port of the servo valve; The valve controller is electrically connected to the motor oil switch valve and is used to control the connection state and valve opening of the motor oil switch valve.

4. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 3, characterized in that: The accumulator group also includes a pilot oil accumulator and a pilot oil switch valve, wherein: The oil outlet of the oil source is connected to the motor oil accumulator and the pilot oil accumulator in sequence through a hydraulic pipeline, a first one-way valve is provided between the motor oil accumulator and the pilot oil accumulator, and the oil flows in a direction from the motor oil accumulator to the pilot oil accumulator; The pilot oil accumulator is connected to the control input port of the servo valve through a hydraulic pipeline; the pilot oil switch valve is arranged on the hydraulic pipeline between the pilot oil accumulator and the control input port of the servo valve; The control output port of the servo valve is connected to the recovery oil tank through a hydraulic pipeline; The valve controller is electrically connected to the pilot oil switch valve and is used to control the connection state and valve opening of the pilot oil switch valve.

5. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 3, characterized in that: The accumulator group also includes a unloading throttle valve and an unloading solenoid valve, wherein: The motor oil accumulator is connected to the recovery oil tank through a hydraulic pipeline, and the unloading throttle valve and the unloading solenoid valve are sequentially arranged on the hydraulic pipeline between the motor oil accumulator and the recovery oil tank; The valve controller is electrically connected to the unloading throttle valve and the unloading solenoid valve respectively, and is used to control the connection state and valve opening of the unloading throttle valve and the unloading solenoid valve.

6. A high-torque, high-speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 5, characterized in that: The accumulator group also includes an oil supply valve and a manual unloading valve, wherein: The oil supply valve is arranged on the hydraulic pipeline between the oil output port of the oil source and the motor oil accumulator; the valve controller is electrically connected to the oil supply valve and is used to control the connection state and valve opening of the oil supply valve; The motor oil accumulator is connected to the output end of the unloading solenoid valve through a hydraulic pipeline. The manual unloading valve is arranged on the hydraulic pipeline from the motor oil accumulator to the output end of the unloading solenoid valve, and the manual unloading valve is in a normally closed state.

7. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 6, characterized in that: The motor servo system further comprises a first safety valve, a second safety valve and a third safety valve, wherein: The first safety valve is arranged on the first pipeline, and the two ends of the first pipeline are respectively connected to the motor oil accumulator and the oil input port of the recovery tank; The second safety valve is arranged on the second pipeline, and the two ends of the second pipeline are respectively connected to the third port of the servo valve and the oil input port of the recovery tank; The third safety valve is arranged on the third pipeline, and two ends of the third pipeline are respectively connected to the fourth port of the servo valve and the oil input port of the recovery tank.

8. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 3, characterized in that: The motor servo system further comprises a first pressure sensor, a second pressure sensor, and a third pressure sensor, wherein: The first pressure sensor is located on a hydraulic pipeline connected to the motor oil accumulator and is used to detect the oil pressure of the motor oil accumulator; The second pressure sensor is located on a hydraulic pipeline connected to the first oil delivery port of the vane motor assembly, and is used to detect the oil pressure of the first oil delivery port of the vane motor assembly; The third pressure sensor is located on the hydraulic pipeline connected to the second oil delivery port of the vane motor assembly, and is used to detect the oil pressure of the second oil delivery port of the vane motor assembly; The valve controller is electrically connected to the first pressure sensor, the second pressure sensor, and the third pressure sensor.

9. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 2, characterized in that: The length of the hydraulic pipeline from the third port of the servo valve to the first oil delivery port of the first vane motor and the second vane motor is equal, and the length of the hydraulic pipeline from the fourth port of the servo valve to the second oil delivery port of the first vane motor and the second vane motor is equal, so that the hydraulic oil supplied by the servo valve to the first vane motor and the second vane motor arrives at the same time.

10. A high torque high speed blade swing motor servo system for aircraft landing gear testing as claimed in claim 2, characterized in that: The first vane motor and the second vane motor both include a cylinder body and a motor shaft, the motor shaft passes through the cylinder body, a plurality of fixed blades are arranged at intervals on the inner wall of the cylinder body, and movable blades are arranged on the motor shaft and are respectively located between two adjacent fixed blades, each movable blade divides the cavity between two adjacent fixed blades into a first oil cavity and a second oil cavity, and the first oil cavity and the second oil cavity in the cylinder body are alternately arranged, the first oil delivery port is connected to the first oil cavity, and the second oil delivery port is connected to the second oil cavity.

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